EP0651174A1 - Amortisseur réglable pour véhicules - Google Patents

Amortisseur réglable pour véhicules Download PDF

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Publication number
EP0651174A1
EP0651174A1 EP94115256A EP94115256A EP0651174A1 EP 0651174 A1 EP0651174 A1 EP 0651174A1 EP 94115256 A EP94115256 A EP 94115256A EP 94115256 A EP94115256 A EP 94115256A EP 0651174 A1 EP0651174 A1 EP 0651174A1
Authority
EP
European Patent Office
Prior art keywords
damping
valve
vibration damper
pressure
valves
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP94115256A
Other languages
German (de)
English (en)
Other versions
EP0651174B1 (fr
Inventor
Zhen Dr. Huang
Klaus Dipl.-Ing. Schmidt
Hans Dipl.-Ing. Scheerer
Andreas Dipl.-Ing. Opara
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Daimler Benz AG
ThyssenKrupp Bilstein GmbH
Original Assignee
Daimler Benz AG
Mercedes Benz AG
August Bilstein GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Daimler Benz AG, Mercedes Benz AG, August Bilstein GmbH filed Critical Daimler Benz AG
Publication of EP0651174A1 publication Critical patent/EP0651174A1/fr
Application granted granted Critical
Publication of EP0651174B1 publication Critical patent/EP0651174B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/44—Means on or in the damper for manual or non-automatic adjustment; such means combined with temperature correction
    • F16F9/46—Means on or in the damper for manual or non-automatic adjustment; such means combined with temperature correction allowing control from a distance, i.e. location of means for control input being remote from site of valves, e.g. on damper external wall

Definitions

  • the invention relates to a controllable vibration damper, consisting of a damper cylinder filled with damping fluid, in which a damping piston, which is connected to a piston rod and is provided with pressure-dependent valves for the rebound and compression stages, slides, which divides the damper cylinder into two working spaces, and which has a controllable outer one Damping valve system for adjusting the damping force of the vibration damper is provided, which in conjunction with the pressure-dependent valves on damping pistons of the vibration damper in tension and compression stages enables four characteristic curves of the damping force, the damping valve system provided with two flow connections having damping valves, each consisting of a pressure-dependent valve for tension - And pressure stage and an electromagnetically controllable, cooperating with at least one passage, axially movable control slide, the damping valves coaxially against each other r are arranged in a substantially cylindrical valve housing and can be connected to one another via flow channels.
  • the object of the invention is to provide the flow connections of the damping valve system in such a way that, depending on the application, the damping valve system can be connected in a simple manner as a bypass valve or in a level control to the vibration damper or the level control device and can also be arranged at such a point in the vehicle at which the known damping valve system cannot be used for reasons of space.
  • At least one of the flow connections for the damping liquid is guided axially into the damping valve system via the end face of the valve system.
  • the damping valve has two axial flow connections.
  • An embodiment of the damping valve system provides that one of the flow connections is a direct connection to the pressure-dependent valve and the passage of the one damping valve controlled by the valve spool and the other of the flow connections is a direct connection to the pressure-dependent valve and the passage of the second damping valve controlled by the valve spool having.
  • the electromagnetically controllable, axially movable control slides working with at least one passage are arranged axially on the outside and the pressure-dependent valves are arranged axially on the inside in the valve housing.
  • At least one of the control slides can be arranged with its electromagnetic drive around the flow connection or at least one of the flow connections can be guided radially around the control slide and its electromagnetic drive.
  • Another advantageous embodiment of the invention consists in that the electromagnetically controllable, axially movable control slides, which cooperate with at least one passage, are arranged axially inside and the pressure-dependent valves axially outside in the valve housing.
  • This arrangement of the damping valves has the particular advantage that the electrical connections of the electromagnetic drives can be routed to the outside via a common plug connection.
  • the flow channel connecting the two coaxially arranged damping valves is passed through the annular valve slides and their electromagnetic drives.
  • the damping valve system has a radial and an axial flow connection
  • the flow connections can advantageously be acted upon in all directions of the damping valve system in the direction of pull and outflow.
  • a controllable single-tube vibration damper which essentially consists of a damper cylinder 33 and a piston rod 37 immersed in the damper cylinder and ending in a damping piston 36 equipped with pressure-dependent valves 34, 35, which is guided by the guiding and sealing unit 38 in the damper cylinder 33 is passed.
  • the damping piston 36 divides the damper cylinder 33 filled with damping fluid into two working spaces 39, 40.
  • the damping valve system 6 connected in this exemplary embodiment between the working space 40 and a spring accumulator (not shown) of a level control system is arranged and points with its valve housing 5 with a small center distance on the outer wall of the damper cylinder 33 two axial flow connections 14 and 15, of which the flow connection 14 is connected to the vibration damper via a flowable connecting part 41 and the flow connection 15 is guided to the spring accumulator (not shown).
  • the damping valve system shown in FIG. 2 consists of a valve housing 5 consisting of a tube section, in which two damping valves 2 are arranged coaxially with respect to one another.
  • Each of the damping valves consists of an electromagnetically controllable, axially movable control slide 9, 10 cooperating with a passage 3, 4 and a pressure-dependent valve 7, 8, each of the pressure-dependent valves 7, 8 consisting of two spring-loaded disc valves 7a, 7b, acting in opposite flow directions. 8a, 8b, which open more or less depending on the damping fluid pressure.
  • the control slides 9, 10 are each moved by an electromagnet 11 and are arranged such that in the de-energized state of the electromagnets 11, the passages 3, 4 are closed and opened when actuated. This ensures that in the event of a fault, e.g. B. power failure or cable break, the damping force of the vibration damper is automatically switched to the hardest damping force characteristic.
  • the flow channel 1 between the passages 3, 4 adjustable by the control spools 9, 10 runs between the outer wall of a tube 12 arranged in the valve housing 5 and the inner wall of the valve housing 5, the tube 12 simultaneously forming the valve interior 18 receiving the pressure-dependent valves 7, 8 .
  • the flow channel 1 furthermore has at least one passage 13 to the valve interior 8 between the pressure-dependent valves 7, 8.
  • the controllable connection to the vibration damper and when used in a level control to the level control device is established via the flow connections 14, 15.
  • the flow connections are formed by the pipe sections 20, 21 inserted into the damping valve system 6 on the end faces 16, 17, both of which are shown in FIG the electromagnets 11 and the annular control slide 9, 10 are arranged around the pipe sections 20, 21.
  • the flow connections 14, 15 end in the valve interior 18 and thus have a direct connection to the respective pressure-dependent valve 7, 8 and the corresponding passage 3, 4 controlled by the control slide 9, 10.
  • the softest characteristic curve is generated when both electromagnets 11 are activated and control spools 9, 10 open passages 3 and 4. Streams the Damping fluid via the flow exclusion 15 in the damping valve system 6, the mode of operation is opposite.
  • FIG. 3 Another embodiment of the damping valve system is shown in FIG. 3.
  • the flow channel 1 is formed here by a pipe 20 arranged in the valve housing 5 between the passages 3, 4 adjustable by the control slides 9, 10 and divided between the pressure-dependent valves 7, 8 to form the passage 13 to the valve interior 18.
  • the tube parts 20a and 20b simultaneously carry the pressure-dependent valves 7 and 8.
  • the flow connections 14, 15 are formed by the end part 23, 24 of the valve housing 5, which has an opening, and between the housing 25 of the electromagnets 11 and the inner wall of the valve housing 5 formed flow channels formed.
  • FIG. 3 shows one possibility of how the electrical connections 26 of the electromagnets 11 can be led out of the damping valve system 6 in the embodiment according to FIG. 3.
  • the end parts 23, 24 hold the electromagnets 11 and the electrical connections 26 via the housing 25 led through the end parts 23, 24 to the outside.
  • valve spools 9, 10 and the electromagnets 11 are arranged coaxially with respect to one another axially on the inside and the pressure-dependent valves 7 and 8 are arranged axially on the outside in the divided valve housing 5, and the pressure-dependent valves 7 and 8 are each axially outside in one a housing 27 formed valve interior 18a and 18b.
  • the housings 27 In order to form the direct connection from the flow connections 14 and 15 to the respective pressure-dependent valves 7 and 8, the housings 27 have at least one bore 28, 31.
  • the direct connection from the flow connections 14, and 15 to those of the Control spools 9, 10 adjustable passages 3, 4, or at least one further bore 29 or bores are made through the bores 28 or 31 in the housing 27. 32 and a flow channel 19 formed between the housing 27 and the valve housing 5.
  • a flow channel 30 creates the connection between the two damping valves 2.
  • the damping liquid flowing in, for example, via the flow connection 14 flows through the bore 28, the pressure-dependent valve 7, the flow channel 30, the pressure-dependent valve 8 and the bore 31 to the flow connection 15 and generates the hardest characteristic.
  • Another line of damping force is generated when the valve spool 9 opens the passage 3, then the damping fluid flows through the bore 28, the valve interior 18a, the bore 29, the flow channel 19, the passage 3, the flow channel 30 and via the pressure-dependent valve 8 to Flow connection 15.
  • the valve slide 10 opens the passage 4, the passage 3 is closed, however, the damping liquid flows through the pressure-dependent valve 7, the flow channel 30, the passage 4, the flow channel 19, the bores 32 and 31 to the flow connection 15 and thus realizes one third characteristic.
  • the softest characteristic curve is generated when both passages 3 and 4 are open, then the pressure-dependent valves 7 and 8 are bridged and the damping liquid flows from the flow connection 14 via the open passages 3 and 4 to the flow connection 15.
  • the damping valve system 6 has a radial flow channel 14 to the working space 40 of the vibration damper and an axial flow channel 15 to the spring accumulator (not shown). (Fig. 6)

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Vibration Prevention Devices (AREA)
  • Vehicle Body Suspensions (AREA)
  • Fluid-Damping Devices (AREA)
EP94115256A 1993-10-29 1994-09-28 Amortisseur réglable pour véhicules Expired - Lifetime EP0651174B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4336950 1993-10-29
DE4336950A DE4336950C2 (de) 1993-10-29 1993-10-29 Regelbarer Schwingungsdämpfer für Kraftfahrzeuge

Publications (2)

Publication Number Publication Date
EP0651174A1 true EP0651174A1 (fr) 1995-05-03
EP0651174B1 EP0651174B1 (fr) 1998-12-16

Family

ID=6501326

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94115256A Expired - Lifetime EP0651174B1 (fr) 1993-10-29 1994-09-28 Amortisseur réglable pour véhicules

Country Status (5)

Country Link
EP (1) EP0651174B1 (fr)
AT (1) ATE174669T1 (fr)
DE (2) DE4336950C2 (fr)
ES (1) ES2070813T1 (fr)
GR (1) GR950300026T1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1217250A2 (fr) 2000-12-23 2002-06-26 Continental Aktiengesellschaft Amortisseur de vibrations réglable
WO2017016867A1 (fr) * 2015-07-27 2017-02-02 Thyssenkrupp Bilstein Gmbh Amortisseur de vibrations pour un véhicule automobile

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4445705B4 (de) * 1994-12-21 2005-03-03 Zf Sachs Ag Schwingungsdämpfer mit verstellbarer Dämpfkraft
DE19731138C2 (de) * 1997-07-21 2002-06-13 Zf Sachs Ag Dämpfkraftveränderbarer Schwingungsdämpfer
DE19733622C2 (de) * 1997-08-04 2002-11-14 Zf Sachs Ag Schwingungsdämpfer mit veränderbarer Dämpfkraft

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4746106A (en) * 1986-08-15 1988-05-24 Nhk Spring Co., Ltd. Car suspension system
DE4125316C1 (fr) * 1991-07-31 1992-10-01 Boge Ag, 5208 Eitorf, De
US5180039A (en) * 1989-07-06 1993-01-19 Fichtel & Sachs Ag Fluid passage unit

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3800288C1 (en) * 1988-01-08 1989-06-22 Boge Ag, 5208 Eitorf, De Valve arrangement for a hydraulic controllable vibration damper
JP2626176B2 (ja) * 1990-05-31 1997-07-02 日産自動車株式会社 能動型サスペンション
DE4216987C2 (de) * 1992-01-17 1994-02-10 Bilstein August Gmbh Co Kg Regelbarer Schwingungsdämpfer für Kraftfahrzeuge

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4746106A (en) * 1986-08-15 1988-05-24 Nhk Spring Co., Ltd. Car suspension system
US5180039A (en) * 1989-07-06 1993-01-19 Fichtel & Sachs Ag Fluid passage unit
DE4125316C1 (fr) * 1991-07-31 1992-10-01 Boge Ag, 5208 Eitorf, De

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1217250A2 (fr) 2000-12-23 2002-06-26 Continental Aktiengesellschaft Amortisseur de vibrations réglable
DE10065184A1 (de) * 2000-12-23 2002-07-11 Continental Ag Regelbarer Schwingungsdämpfer
US6702075B2 (en) 2000-12-23 2004-03-09 Continental Aktiengesellschaft Controllable shock absorber
DE10065184B4 (de) * 2000-12-23 2005-03-24 Continental Aktiengesellschaft Regelbarer Schwingungsdämpfer
WO2017016867A1 (fr) * 2015-07-27 2017-02-02 Thyssenkrupp Bilstein Gmbh Amortisseur de vibrations pour un véhicule automobile
CN107850165A (zh) * 2015-07-27 2018-03-27 蒂森克虏伯比尔斯坦有限公司 用于机动车辆的振动阻尼器
US10487902B2 (en) 2015-07-27 2019-11-26 Thyssenkrupp Bilstein Gmbh Vibration damper for a motor vehicle
CN107850165B (zh) * 2015-07-27 2019-12-06 蒂森克虏伯比尔斯坦有限公司 用于机动车辆的振动阻尼器

Also Published As

Publication number Publication date
DE4336950C2 (de) 1997-01-16
DE59407490D1 (de) 1999-01-28
ATE174669T1 (de) 1999-01-15
EP0651174B1 (fr) 1998-12-16
ES2070813T1 (es) 1995-06-16
GR950300026T1 (en) 1995-06-30
DE4336950A1 (de) 1995-05-04

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